Power system utilizing free-piston engine and torsionally resonant transmission

ABSTRACT

A kinetic power system for driving automotive vehicles or similar apparatus having variable load and speed requirements. A novel free-piston engine functioning as a self-tuning sonic oscillator comprises the prime mover. Alternatively, a conventional rotary prime mover may be employed to drive an orbiting-mass oscillator at the system&#39;&#39;s input. The oscillator output drives a torsion-spring resonator which functions as a torque converter. The oscillatory output of the torque converter is rectified into unidirectional rotary motion that may be applied directly to the output load.

United States Patent [191 Bodine Apr. 23, 1974 ENGINE AND TORSIONALLY RESONANT TRANSMISSION Albert G. Bodine, 13180 Mulhalland Dr., Beverly Hills, Calif. 90210 Filed: Jan. 5, 1973 Appl. No.: 321,285

Inventor:

0.5.01 Int. 0. Field of Search 60/1; 74/61, 63, 89

References Cited UNITED STATES PATENTS 10/1926 Clemens 74/61 11/1939 Dake 60/1 X 11/1970 Shatto, Jr 60/1 POWER SYSTEM UTILIZING F REE-PISTON v Primary ExaminerEdgar M. Geoghegan Assistant Examiner-Allen M. Ostrager Attorney, Agent, or Firm-Robert E. Geauque ABSTRACT A kinetic power system for driving automotive vehicles or similar apparatus having variable load and speed requirements. A novel free-piston engine functioning as a self-tuning sonic oscillator comprises the prime mover. Alternatively, a conventional rotary prime mover may be employed to drive an orbitingmass oscillator at the systems input. The oscillator output drives a torsion-spring resonator which functions as a torque converter. The oscillatory output of the torque converter is rectified into unidirectional rotary motion that may be applied directly to the output load.

20 Claims, 11 Drawing Figures PATENTEDAPR 23 I974 SHEET 2 BF 6 ill/1 Ar m PATENTEDAPR 23 mm (1805; 5 14 SHEET 3 BF 6 "ATENTEDAPR 23 I974 SHEET h UF- 6 ZJATENTEBAPR 2 3 I974 SHEET 5 BF 6 ilvloe ATENTEDAPRZB mm (1805; 514

SHEET 8 UF 6 1 POWER SYSTEM UTILIZING FREE-PISTON ENGINE AND TORSIONALLY RESONANT TRANSMISSION BACKGROUND OF THE INVENTION There is described in my copending U. S. patent application Ser. No. 290,217 filed Sept. 18, 1972, a torque converter transmission system which automatically matches a source of oscillatory kinetic energy to a variable load. The present invention is an extension of that concept wherein the torque converter is incorporated into a fully integrated power system encompassing all elements from the prime mover to the ultimate load.

- While the piston-driven crankshaft internal combustion engine and the hydraulicautomatic transmission, have enjoyed a long history of commercial success, it is recognized by those versed in the art that there is a need for a power system which would overcome the well-known deficiencies of such engine/transmission systems. Specifically, there is a need for a wider range of operating speeds and torques, a substantial reduction in the number of moving parts, an abatement of noise and vibration, and a decrease in the manufacturing costs of rotating-shaft power plants. Much effort has gone into the development of a new generation of engine systems to supplant the aforementioned conventional type of internal combustion engines. The use of turbines as a direct replacement has been disappointing in many applications. The emergence of the socalled"rotary engine is indicative of the trend tov engines having fewer moving parts and a more favorable weight-to-power ratio. However, the high manufacturing costs and the difficulty of making reliable seals for the moving parts have been an impediment to the universal acceptance of such engines.

Aside from the engine per se, the problems of effectively coupling the output of the engine to the load have been similarly difficult. What is needed is a stepless torque converter of high efficiency, and having a range of speeds and torques wider than that afforded by conventional fluid drivesor hydraulic automatic transmissions. Such a torque converter would permit optimization of the operating regime of the prime mover, whatever type it may be.

While considered as being especially suitable for use in automotive vehicles, the present invention relates to the entire field of self-contained rotating-shaft power systems characterized by the requirement for a continuously variable range of power and speed demands.

SUMMARY OF THE INVENTION There is provided by the preferred embodiment of the present invention a novel and improved prime mover comprising a selftuning orbiting sonic oscillator. This oscillator is embodied in a novel free-piston engine having oscillating pistons that actas torsional impulse drivers moving cyclically along the circumferential path of a partial torsional orbit. The cylinder body or external case enclosing the pistons is closely coupled to a torsional resonator of the type described in the aforementioned copending application entitled Torque Converter Transmission System. In another embodiment of the invention an orboresonant or orbiting mass oscillator and its associated power source are used as the means for driving the resonating transmission system. Torsional oscillations from the oscillatory source generate a sonic wave pattern in an elastic torsion member comprising the torque converter. The torsion member terminates in a sonic rectifier whose function is to rectify the oscillatory torsional motion of the member into a continuous unidirectional rotary drive motion. By using full wave rectification (as in an electrical circuit), both directions of turning of the torsional oscillation cycle are made to deliver continuous rotary energy to the output shaft. The rectifier also performs an important impedance matching function as the termination of the torsion member resonator. Properly terminated so as not to have a characteristic impedance which is too high, the resonator will automatically shift its resonant pattern (viz. mode of vibration) in response to changes in the load impedance seen at the rectifier. It is this automatic shifting of its resonant pattern that results in the desired automatic torque converter action.

The novel and improved free-piston engine of the invention is basically a one-moving part thermodynamic power plant. The moving part is an unconstrained piston in a'cylinder driven back and forth in response to a combustion cycle. The periodic combustion yields the periodicity for the desired torsional oscillation. The mass inertia of the oscillating piston provides the driving energy for the torsional resonator. The power developed is largely determined by the phase angle between the piston displacement cycle and the torsional displacement cycle of the cylinder assembly. No direct mechanical connection is needed from the piston to the remainder of the system, since it merely delivers its power through its reactance, via the cylinder assembly. The cylinder assembly oscillates through an arcuate orbit and also comprises the main flywheel" in the resonant circuit.

The resonating circuit accomplishes the desired torque multiplication by working from the reaction of the cylinder assembly. Thus, the output torque reaction is not transmitted through countershafts, gears, and

bearings (with their attendant freictional forces) as in prior art power systems. In the present invention the torque reaction is developed by a lever effect working from dynamically moving massses. In gear-type transmission systems of the prior art, for each foot pound of torque available at the output shaft, there is an equal foot pound of torque developed in the transmission case. This internal torque results from a gear step-up such that side gears within the gear step-up are delivering hightorque to the case. This torque is delivered to the case via bearings which give the above-mentioned disadvantage of accomplishing high torque by having high friction.

In contrast, the operation of the present invention is analogous to the recoil from a gun wherein the dynamics exist in the discharged bullet. That is, the torque is developed from the reaction. produced by moving masses. An advantage is gained thereby since there are no highly loaded bearings and there is, of course, very little energy loss. Speed and torque demands can be met throughout a very wide range and can be continuously adjusted in a stepless manner. Since energy is deliveredv from an oscillator that is inductively coupled to the load, the engine can keep on turning even though the output shaft is locked.

It is therefore an object of the invention to provide a novel and improved rotary power plant having a minimum of moving parts, a very wide stepless range of speed and torque performance, and which is light in weight, compact, and low in cost.

Another object of the invention is to provide a novel and improved combination of a free-piston sonic oscillator, an automatic sonic torque converter, and a bidirectional-to-unidirectional motion converter.

Still another object of the invention is to provide a kinetic power system having fewer parts than systems heretofore intended to accomplish generally similar functions.

Yet another object of the invention is to provide a novel and improved rotary power plant which is fully balanced, virtually vibrationless, and which is of low cost.

It is yet another object of the invention to provide a rotary power plant of novel and improved design which has exceptionally low engine starting torque demands.

Another object of the invention is to provide a novel power plant having improved secondary power features as are suitable for driving system accessories.

These and many other objects and features of the present invention will be disclosed in the specification which follows and the accompanying drawings.

BRIEF DESCRIPTION OF THE DRAWINGS FIG. 1 is a somewhat schematic diagram of resonant torque wrench, useful in describing the underlying theory of the invention;

FIG. 2 is a diagrammatic illustration of an orbiting oscillator and a resonant torsional torque converter of the type herein considered;

FIG. 3 is a front elevational view, partly in section, of the oscillator portion of the apparatus of FIG. 2;

FIG. 4 is a cross-sectional view of the apparatus of FIG. 3, taken along line AA thereof;

FIG. 5 is a front elevation view of an orboresonant oscillator suitable for driving an automatic transmission system constructed in accordance with the invention;

FIG. 6 is a cross-sectional view of the apparatus of FIG. 5, taken along line A-A thereof;

FIG. 7 is a sectional view taken along line 8-8 of FIG.

FIG. 8 is a sectional view taken along line C-C of FIG. 6;

FIG. 9 is a schematic diagram of power system constructed in accordance with the invention and which employs an orboresonant oscillator;

FIG. 10 is a side elevation view of a two-cycle, freepiston, engine-oscillator constructed in accordance with the invention, for driving the sonic torque transmission; and

FIG. 11 is a sectional view taken along line AA of FIG. 10.

DESCRIPTION OF THE PREFERRED EMBODIMENTS Referring to FIG. 1, there is shown, in somewhat diagrammatic form, the basic or fundamental elements of the invention. This representation of the invention, which may be referred to as a resonant torque wrench, will be useful in understanding the underlying theory. In essence, the invention comprises a resonator (lever) of the mechanical type, with a mechanical oscillator at one end and an acoustic rectifier at the other end. The mechanical resonator consists of elastic resonant bar 2 which is driven (excited) by mechanical oscillator 3. The oscillator 3 may be one of the types described in my U. S. Pat. Nos. 2,960,314 or 3,217,551 and which is capable of imparting acoustic vibrational energy to the end of the bar 2 to which the oscillator is connected. A lateral bending resonant vibration is imparted to bar 2 by operation of oscillator 3. The lower end of bar 2 is mechanically coupled to a unidirectional clutch 4, which may be a conventional sprag clutch. This clutch acts on output shaft 5 to impart unidirectional rotary motion thereto. Oscillator 3 is, effectively, freely supported on the upper end of bar 2, and the entire assembly is supported upon rigid base 6 via resilient support spring 7.

Operation of oscillator 3 causes resonant lateral bending vibration (as indicated by arrows 8 and 9) of bar 2, thereby resulting in torsional impulses being delivered from the lower end of the bar 2 to clutch 4. The action of the clutch rectifies the oscillatory lateral vibrations to deliver rotary motion to shaft 5. That is, the clutch 5 engages and turns shaft 5 whenever the resonant bar 2 is tending to cause a turning motion around the mounting of clutch 4. When the bar 2 reverses its direction of motion, the clutch 4 disengages so that the shaft 5 will not be turned backwards on the alternate half cycles of operation. Thus, shaft 5 is driven only during one-half of each of the resonant vibration cycles of bar 3.

Vibratory lateral motion caused by oscillator 3 at the top end of the bar 2 results in uniformly directed rotary motion at the bottom end of the bar. Torque delivered to shaft 5 is carried in reaction by spring 7; otherwise, if there were no resistance, bar 2 would tend to rotate around a stationary shaft 5. Reaction of spring 7 holds bar 2 from travelling about shaft 5, with the result that shaft 5 has to develop a motion of its own.

One end of bar 2 will be bending (viz., turning) in one direction, while the other end is bending in the opposite turning direction. There will be a nodal region somewhere between the ends of the resonator bar 2 where the turning motion is neutral. As will be explained more fully hereinafter, the automatic shifting of the location of this nodal region along the length of the resonator bar is the phenomenon that provides the automatic torque converter function. At any one instant, all of the turning motion is in one direction on one side of the node, and will be on the other side of the node when the turning motion is in the opposite direction. The oscillations reverse at the cyclic resonant frequency of the system. Torque multiplication results from the fact that the amplitude of motion increases with distance from the node, and the closer to the node the greater the cyclically turning impulse force. It is, then, analogous to a movable fulcrum for a lever. Therefore, by shifting the position of the node along the resonator bar, force may be traded for motion (and conversely) in the manner of an automatic transmis- The appearance of a torque load on the output shaft 5 acts as a restraint which is reflected back through the unidirectional clutch 4 so as to present an increased acoustic impedance at the output (lower) end of the bar 2. It is this action which causes the node of the bar 2 to shift and thereby result in an increased force, commensurate with the decreased amplitude of motion, into the clutch 4 and on into the output shaft 5. That is, bar 2 under these conditions will run as a resonant member with a node near the bottom end and an antinodenear the top end. Accordingly, as shaft 5 experiences greater and greater resistance of rotating motion, the node will move further and further down on the resonant bar 2. As a result, the oscillator 2 can move with a larger displacement or stroke. I

The drive frequency of the oscillator 3 is initially set to correspond to the resonant frequency of the bar 2 when the lower end (output end) is completely locked. This locked load frequency equals the peak power (or governor-controlled) operating speed of the prime mover. Proceeding from the locked load resonant frequency condition, as the lower end of the bar 2 frees up (that is, as the shaft 5 is able to turn easier and easier), the bar 2 will experience a less and less resonant condition. Thus, a decrease in the loading of output shaft 5 results in the bar 2 getting further and further from its resonant condition. Therefore, there will be less and .less multiplicationof torque in the system.

The effect of the system is to try to run the output shaft at a constant speed. This speed drops off only as the power of the prime mover is exceeded. However, the output torque will tend to increase as the output shaft 5 is loaded down in speed (i.e., as the load impedance approaches the locked load condition.)

Because of the variable torque multiplying characteristic of the invention, the input torque to the oscillator can be very much less than the output torque at shaft 5. This is, of course, accomplished by having an appropriately high imput speed into the oscillator.

It is important to note that it is not necessary to operate the oscillator 3 at a frequency which exactly corresponds to locked load conditions. A condition which would be resonant for bar 2 when shaft 5 is completely locked is just one desirable way to operate the system. However, the system can be operated advantageously by having oscillator 3 driven by a prime mover which itself is torque responsive. This may, for example, be a conventional internal combustion engine such as employed in automobiles. Any energy extracted from shaft 5 appears as an acoustic resistive impedance in the resonant circuit. This in turn appears as an increase in the required imput torque tothe oscillator. Accordingly, the prime mover itself will see some increase in the torque load which is in addition to the torque con verter effect of the resonant system.

While the foregoing description of an elementary system constructed in accordance with the invention made reference to a single spray clutch, which is in effeet a half-wave motion rectifier, it will be apparent that a full-wave scheme could readily be employed. The use of a pair of unidirectional clutches'and the required ancillary apparatus, as will be described more fully hereinafter,'will permit both directions of oscillatory imput motion to be converted to useful rotary output motion.

There will now be described an exemplary embodiment of an oscillator suitable for performing the function of oscillator 3 of FIG. 1. Referring to FIG. 2 there is shown a main case 11 which houses and supports the system. Input shaft 12 is rotatably supported in a journal 13 carried in one end wall of case 11'. Shaft 12 is driven in continuous rotation by a prime mover 10, as

shown in FIG. 4, of any suitable and well-known type. Oscillator housing 14 is mounted within case 11 for oscillatory arcuate movement'about the axis of shaft l2,

and carries a pair of shafts l5 and 16, and weights 17 and 18 are driven via cog belts 22 and 23, respectively. Belts 22 and 23 are driven from gears 20 and 20 as shown in FIG. 4 which are mounted for rotation with input shaft 12. Rotation of the input shaft 12 will result in rotation of weights 17 and 18 in the same direction, but since they arephased 180 out of phase, they will give torque couple when they are from being swung either all outwardly or all inwardly. Their torque couple will be mutually neutralized when they are both swung all of the way apart or all of the way towards each other. This relationship is best seen in FIG. 3. The torque couple effect will be more fully described hereinafter in connection with FIG. 7.

The inductive reaction from swinging weights l7 and 18 is transmitted to housing 14. The reaction in bearings 24-27, which support corresponding shafts l5 and 16, causes oscillator housing 14 to have a torsional motion about its central axis which is coaxial with shaft 12. This torsional oscillation of housing 14 in turn reacts on springs 28-28 and 29-29 which couple housing 14 to pulse arms 31 and 31'. Pulse arm 31 is mounted on torsion shaft 32 for movement therewith. Shaft 32 is secured to central mandrel 33 which in turn is joumalled in bearing 34 carried in main case 1 1. This assembly comprises a one-spring, two-mass resonant system in which the first mass is that associated with housing 14, the system spring consists of springs 28-28 and 29-29 in the middle of the system, and the second mass is that which is associated with pulse arm 31-31 and torsion shaft 32. Springs 28-28 and 29-29 are the functional equivalent of the elastic resonant bar 2 in the simple apparatus of FIG. 1.

The oscillating torque developed by the swinging weights 17 and 18 is delivered through shaft 32, which is an extension of reaction mandrel 33.

Shaft 32 drives sprag clutch 35 having peripheral output gear 36, which in turn drivingly engages gear 37. Shaft 38 is driven by gear37 in a single direction as a result of the one-way action of sprag clutch 35.

The far end of shaft 32 drives the inner portion of sprag clutch 39 and will deliver a one-way torque to the outer portion thereof whenever shaft 32 is moving in one turning direction. The outer portion of sprag clutch 39 will remain stationary when the shaft 32 is turning in the other direction. When shaft 32 is turning in the non-driving direction with respect to clutch 39, it delivers the other half of its oscillatory driving motion through clutch 35 to shaft 38. Cog belt 41, carried on pulleys 42 and 43, drives output shaft 44. The outer portion of clutch 39 is also connected to output shaft 44. Thus there is provided a full-wave rectification system whereby output shaft receives a constant unidirectional torque from oscillating shaft 32. The outputs from sprag clutches 35 and 39 are added (each being responsive to one-half of the oscillatory input cycle) to give a continuous delivery of rotary motion from theoutput shaft44. Being a full-wave system, there is no need for .the torque reaction spring 7 shown and described in connection with FIG. 1. The full torque reaction delivered through output shaft 44 is carried by the dynamic reaction of oscillator weights 17 and 18.

The various possible operating modes of the apparatus of FIG. 4 will now be discussed. First assume that the back torque presented by a load connected to output shaft 44 is very light. Under this condition very little output torque is needed to turn the shaft 44. In this mode of operation the input shaft 12, which is continuously rotated by the prime mover 10, tends to cause housing 14 to rotate through a full circle almost in step with shaft 12. This occurs because oscillator weights 17 and 18 have a tendency to swing to their outside position and stay there. Moreover, there is a certain amount of windage and friction in the oscillator assembly. As a result, either clutch 35 or 39 will tend to release and not deliver torque while the remaining clutch transmits torque through the full circle of rotation. The effect is essentially the same as if shaft 12 were direct coupled to output shaft 44.

Next assume that an appreciable torque load exists at output shaft 44. This torque load is reflected backwards through the system to oscillator housing 14. As a result, oscillation of housing 14 begins to slow down with respect to input shaft 12. It is this difference in speed between housing 14 and shaft 12 that causes oscillator weights 17 and 18 to turn through their respective orbital paths. That is, the oscillator weights 17 and 18 are driven by reason of the torque transmitted through cog belts 22 and 23.

As used herein, the word torque is intended to encompass the overall effect including the longitudinal delivery of force as in the case of that imparted to springs 28-28 and 29-29. However, since this longitudinal delivery of force is in effect a tangential force to a center about shaft 12, it can be considered as a periodic. torque.

The greater the torque load appearing at the output 44, the greater will be the difference between the speed of shaft 12 and that of housing 14. The result of this will be that the rotary motion of the weights l7 and 18 will begin to appear as a torque pulse applied to housing 14, as described previously. The oscillator weights l7 and 18 are capable of delivering a periodic torque, through housing 14, which is substantially greater than the instantaneous torque supplied to the input shaft 12. This output torque from the oscillator is due to the centrifugal force of the weights 17 and 18. The periodic orbiting motion of the orbiting weights results in powerful torque pulses being delivered to housing 14, which are in turn transmitted via springs 28-28' and 29-29' to the reaction pulse arms 31 and 31.

To examine the third mode of operation of the system, assume that the torque load appearing at shaft 44 is increased still further. The effect of this will be a tendency to restrain the motion of clutches 35 and 39, and therefore the motion of shaft 32 as well. In the extreme case, locking output shaft 44 so that it could not turn at all would cause both sprag clutches 35 and 39 to be held in a rigid position. The inability of clutches 35 and 39 to rotate will also prevent shaft 32 from turning. If the pulse arm 31 is held in a fixed position, springs 28 and 29 will see this as a node connection of the springs. Accordingly, each spring (2 8-28 and 29-29) will resonate with maximum freedom at that end which is connected to the oscillator housing 14, and with zero freedom at that end which is connected to the pulse arm 31. Springs 28-28 and 29-29' will then act as if they were part of a system that is one-quarterwave length long. In this locked load condition" the output shaft 44 will experience maximum torque and the system yield a maximum amount of torque multiplication. This is because the resonating springs 28-28 and 29-29' act as maximum acoustic levers, such that their nodes or point of maximum force application occurs on pulse arms 31 and 31'. In this condition the output of the springs presents a maximum acoustic impedance, and the oscillator housing 14 will move with maximum freedom, thereby delivering very high torque pulses to pulse arms 31-31. These high energy transmitted torque pulses ultimately are converted to a unidirectional maximum torque at output shaft 44.

If the output load at shaft 44 should then decrease somewhat, the system will automatically respond to the commensurately reduced impedance at the pulse arms 31-31'. Also, the resonant springs 28-28 and 29-29' see a lower impedance at their terminations at arms 31-31'. The ends of the springs which are in contact with the reaction arms 31-31 will move with greater motion and correspondingly lower force as a result of this lowering of impedance. In actuality the node shifts back a ways on the springs. With this shift in the location of the node, the arms 31-31 act more like the end of the springs where they connect to housing 14. When the impedance is the same at both ends, then the springs will have their node intermediate the ends thereof. As will be appreciated, this node can shift its position automatically through a stepless'range of positions to yield a virtually infinite range of torque-versusspeed ratios for the system. In summary, the invention provides torque multiplication by shifting of the node in the resonant system. Under light load conditions the node will be closer to the oscillator and there will, in effect, be an antinode at the end opposite the oscillator. This antinode results in a relatively high velocity at the output. The imposition of greater load on the output raises the acoustic impedance at the output, thereby causing the resonant system to compensate by having its node shift away from the input and closer to the output. Concurrently there will be a decrease in the amplitude of output motion, as is required by the laws of conservation of energy. This shift of the node towards the output end of the resonator elements tends to place the antinode closer to the oscillator, thereby allowing it to move through a greater amplitude. Under these conditions the oscillator functions in a manner analogous to a constant voltage generator in an electrical circuit. Thus, the horsepower demands placed on the prime mover are more or less constant while keeping the output torque increasing as the motion increases at the oscillator.

There is shown in FIGS. 5-8 a practical construction of a transmission system that incorporates the various features of the apparatus previously described in connection with FIGS. 2-3 into a unitary structure. As seen in the elevation view of FIG. 5, unidirectional rotary output power is obtained from shaft 51 which is journalled in bearing 52. Cover plate 53 encloses one end of transmission housing 54 and also serves to support several of the bearings therein, as is shown in FIG. 6. Cover 55 encloses one end of the oscillator housing 56,

and is secured to cover plate 57 enclosing the other end of the transmission housing 54.

Unidirectional rotary power, from a prime mover (not shown), is supplied to imput shaft 58 which is journalled in bearing 59. Oscillating shaft 61 is coaxially aligned with both the input shaft 58 and the unidirectionally rotating output shaft 51, thus simplifying the incorporation of the system into a vehicle or other ancillary system.

The internal components are essentially the same as those previously described in connection with FIGS.

2-3. Gears 62 and 63 drive gears 64 and 65, respectively, via cog belts 66 and 67, respectively. Shaft 58 is further supported in bearings 68 and 69 which are carried in plates 71 and 72, respectively.

Shaft 73, which is supported by bearings 74 and 75, rotates with gear 65 and turns eccentric weight 76. Similarly, shaft 77 supported by bearings 78 and 79 turns with gear 64 and rotates eccentric weight 81.

Plates 71 and 72 are joined to case number 82 (best seen in FIG. 7) to enclose the oscillator mechanism. Oscillatory motion of the case (elements 71, 72 and 82) is transmitted to shaft 61 via reaction mandrel 83 and supporting springs 84-87, as shown in FIG. 8.

Unidirectional clutch 88 is driven by oscillating. shaft 61 and in turn drives gear 89. This causes shaft .91 to turn in a single direction because of the one-way action of clutch 88. Shaft 91 is supported by bearings 92-95 and also drives gear 96 which is direct-belted to gear 98 via belt 97. The output shaft 51 is turned by gear 98.

Oscillating shaft 61 also drives unidirectional clutch 99 which operates in the reverse direction with respect to clutch 88. The output of clutch 99 directly drives output shaft 51 on alternate half cycles of the motion of shaft 61. Thus, as explained previously, there is provided a full-wave rectification system wherein output shaft 51 is continuously rotated in a given direction and receives a substantially constant torque from oscillating shaft 61. The full torque reaction delivered through the output shaft 61 is carried by the dynamic reaction of oscillator weights 76 and 81. These weights, swinging about shafts 17 and 73, respectively, are capable of delivering considerably greater periodic torque through the case assembly (71, 72 and 82) by bearings 74-75 and 78-79 than is necessarily the input torque applied to shaft 58. This output torque of the oscillator is due to the centrifugal force of the weights 76 and 81 swinging around, and may wellv exceed the instantaneous torque delivered to shaft 58.

As the torque load of shaft 51 increases, the motion of clutches 88 and 99 tends to become restricted. This in turn tends to curtail, the freedom of motion of mandrel 83. Obviously, if the load at shaft 51 were sufficiently great as to prevent its turning at all, the result would be that clutches 88 and 99 would be restrained from moving. As a consequence, shaft 61 and mandrel 83 could not move. the resulting locked load condition is the same as that described at page 21. If the mandrel 83 is held in a fixed position, the springs 84-87 are forced to respond as if their connection to the mandrel were where at a node. Accordingly, each spring 84-87 will resonate with its maximum motion at the end opposite the mandrel 83, namely, the end adjoining the oscillator housing 82. Under this condition, the springs 84-87 respond as if they were part of a resonant system one-quarter wavelength long. This allows the oscillator housing to move with the maximum degree of freedom and deliver the highest possible torque pulses to the reaction arms 101-104 that connect springs 84-87, respectively, to the oscillator case. That is, the output of the springs presents maximum impedance to the output end of the system and results in a maximum torque multiplication. This is because the resonating springs act as maximum acoustic levers wherein theit nodes or point of maximum force application occurs at mandrel 83, which in turn drives shaft 61.

As the loading of the output shaft 51 decreases, there is reflected back through the system (e.g., clutches 88 and 99, and shaft 61) a greater freedom of movement. This lowers the impedance at mandrel 83 and allows the springs 84-87 to see a lower impedance where they interface with the mandrel 83. The consequence is that the nodes shift away from the mandrel end and move towards the ends that are coupled to the oscillator housing.

1 When the impedance is the same at both ends, the springs 84-87 will have their node at their respective centers. As will be appreciated, the node can shift its position with an infinite range of variation, as determined by the impedances appearing in the system. The result is an infinite range of torque variations as between input and output with no step torque effects. It is important to note that only is the adjustment of torque stepless, but is variable through a very wide range greatly exceeding that of conventional prior art transmission systems.

The transmission systems described thus far may have a residual ripple in their output as a result of clutch effects and the like. Since this may be disadvantageous in certain applications, a capacitance in the form of a torque spring may be connected to the output shaft (e.g., shaft 51). Alternatively, an output torsional compliance bar may be employed. Other refinements may be incorporated into an overall system.

Having described both a basic or simplified resonant torque converter and an oscillatory drive therefor, there will now be described the components of a complete power system with the refinements desired in a practical construction. One application for such a system may be for powering an automobile. Referring to FIG. 9, the power source 105, which may comprise a conventional automotive internal combustion engine, drives fluid coupling or automatic clutch 106 (of any suitable and well-known design) via shaft 107. The automatic clutch permits the engine 105 to be completely disengaged from the power train and/or transmission system as may be desired for start up or for engine runup without putting the vehicle in motion. The output shaft108 of clutch 106 drives the central drive gear of a power divider gear box 109. The input power via shaft 108 is divided between gears 111 and 112 which in turn rotate a pair of output drive lines via corresponding universal joints 113-116. Compliant torsion bar 117 interconnects the case of gear box 109 with the case of torsional oscillator 118 and picks up the gear box torque.

Torsional oscillator 118 employs a pair of eccentric weights 121 and 122 which are phased 180 degrees with respect to each other, and driven in the same direction via the input drive lines 123-124. Torsion shaft 125 couples the oscillatory output of oscillator 118 to small flywheel 126, the output of which is coupled to torsion bar 127. The main resonant system includes bar 127 which performs the acoustic lever function discussed in connection with the apparatus of FIG. 1. The output end of bar 127 is transmitted to large flywheel 128 and thence to shaft 129. The oscillatory motion of flywheel 128 and supporting shaft 129 comprises the input to rectifier-torque multiplier 131. The rectified and torque-multiplied output appearing at shaft 132 is imparted to small flywheel 133 and then to the input of rectifier 134.

Rectifier 134 is referenced to the main supporting structure 135 of the system in order that the torque need not be carried by a spring as shown and described in the embodiment of FIG. 1. This grounded rectifier 134 may comprise a sprag clutch that operates in opposition to sprag-clutch rectifier 131. Clutch 131 is the main rectifier clutch for converting the torsional oscillations of elastic bar 127 into a unidirectional rotation which is delivered to rectifier 134. Although the rotary motion delivered to rectifier 134 from rectifier 131 is of steady direction, it is not of steady velocity. The tendency, then, would be for the output to turn back on itself if it were not constrained by rectifier 134 which prevents any reverse turning from the input end of shaft 136. That is, shaft 136 is inched around is a series of pulses in one direction, and is restrained from snapping backwards by rectifier clutch 134. The unidirectional rotation of shaft 136 then comes about from halfvvave rectified pulses delivered through main 'rectifier 131 from the resonant system 127. In the previously described embodiments of the invention shown in FIGS. 2-4 there exists a small but significant output ripple in the rotation of the systems output shaft, nonwithstanding full-wave rectification. As suggested previously, this undesirable ripple can be suppressed by placing an acoustical capacitance in the systems output. In a practical construction this may take the form of a torque spring connected to the output shaft. In the embodiment shown in FIG. 9, shaft 136 may take the form of a torsional-compliance bar which drives inductive flywheel 137 for smoothing of the ripple beyond that obtained from the compliance of shaft (bar) 136. The resulting output will be a very steady, ripple-free, rotary motion through the output shaft beyond flywheel 137.

Fluid coupling 138, which is connected between the output of flywheel 137 and the output shaft 139, permits the system to be disengaged from its load whenever desired. This is of advantage where it is desired to speed up the engine without delivering power to the output.

There is shown in FIGS. 10 and 11 a novel free-piston engine constructed in accordance with the invention, and which may be employed in lieu of the combination of a rotary prime mover and an orbiting-mass oscillator as has been discussed in connection with FIGS. 5-9. In this case, the engine and the oscillator are combined into an integral unit. The basic resonant element in this subsystem comprises elastic resonant bar 141. This is the functional equivalent of bar 2 in the basic system described previously.

There is shown in FIGS. and 11 a free-piston engine of novel design, constructed in accordance with the invention, and which is capable of combining the functions of the prime mover and the torsional oscillator for driving the novel transmission disclosed above. That is, the free-piston engine becomes a torsional 0scillator. The cylinder assembly of the engine is directly coupled to the resonating system. The reaction of explosive combustion within the cylinders, and the motions of the pistons, are in a tangential direction with respect to the output shaft. Thus, torsional pulses are delivered through the cylinder assembly to the output shaft. This results from the cylinder assembly rocking about a symmetrical axis (coaxial with the output shaft), thereby delivering torsional resonant vibrations to the resonating system.

Although free-piston engines can exist in a number of forms, that shown in FIG. 10 is especially suitable for accomplishing the above-described function. By simply having the cylinder assembly directly connected to one end of the resonator, it becomes the input inductance for the resonator. The free pistons within the cylinders, by their inductive reaction deliver energy to the cylinder assembly. The cylinder assembly is, as stated previously, the inductance part of the resonator. This purely inductive coupling is especially desirable because the cylinder assembly can adjust its rotary or torsional stroke to whatever impedance conditions are imposed by the resonator.

Referring to FIG. 10 there is shown a resonant bar 142 which is both the output shaft of the engineoscillator assembly and the input shaft of the resonant transmission system. That is, bar 142 performs the functions of both elements 33 and 34 of FIG. 2, and is a torsionally elastic bar. By reason of its elasticity, it obviates the resonant springs 28-28, 29-29 of the apparatus of FIG. 2. Bar 142 is supported by resilient mounts 143 and 144 which allow the required torsional motion of the bar. Transmission 145 is secured to bar 142 and may comprise the pertinent portions of the apparatus of FIGS. 2-9.

The engine-oscillator comprises a cylinder housing consisting of right and left halves 146 and 147, respectively, as seen in FIG. 11. The center portion of the mating halves of the housing (146-147) clamps onto bar 142 and is fixedly keyed thereto by means of key pins 148 and 149. A bolt flange is provided by means of which the cylinder assembly (146-147) is fastened together. A plurality of bolts, a typical one of which is indicated at 151, extend through the mating bolt flanges and are secured with mating nuts (152). The housing is symmetrical so that it can torsionally oscillate or rock about the axis of bar 142. Also, the housing is provided with four cylindrical chambers for receiving pistons 152-155, respectively. These pistons (152-155) are free to slideably move back and fourth within their respective cylinders in response to the operation of the engine. Pistons 152 and 153 move in unison as a set as do pistons 154 and 155, in a manner to be described hereinafter. It is this oscillation of the pistons which imparts an oscillatory motion (by inductive reaction) of the housing (146-147). Each piston is provided with a plurality of circular piston rings, a typical one of which is indicated at 156, and may be of conventional and well-known construction.

Since each of the four piston-cylinder assemblies is essentially the same (except for its geometric orientation with respect to the others) a typical one will be described in sufficient detail to enable one skilled in the art to comprehend the character of the invention.

A fuel inlet jet 157 is supplied with fuel, such as gasoline, from any suitable supply (not shown). The fuel is aspirated via venturi 158 through carburetor valve 159, and thence through passage 161 into the combustion chamber 162. Note that passage 161 also communicates with combustion chamber 163. Spark plug 164 ignites the air-fuel mixture in chamber 162 thereby driving both piston 154 and piston in the direction of arrow 165. Annular skirt 166 joins pistons 154 and 155 causing them to precisely move in tandem. Skirt 166 also performs another function to be described hereinafter.

The displacement of piston 154 in the direction of arrow 165 will open exhaust port 167 to permit the exhaust of the products of combustion.

The pair of pistons (154-155) are driven in the reverse direction (viz., opposite to arrow 165) by the ignition at spark plug 168. Thus, the free piston set (154-155) is driven by periodic combustion in first combustion chamber 162 and then 163. Timing of ignition may be controlled by any suitable and well-known means, not included in FIG. 11. The alternate firing in combustion chambers 162 and 163 causes the free piston assembly (154, 155, and 166) to oscillate back and forth between the two combustion chambers. The mass reactance of this free piston assembly is delivered to the housing 146-147, and functions as a true inductive oscillator; that is, it is acoustically the equivalent of the swinging-weight oscillator of FIG. 2. The mass reactance of the oscillating pistons (154-155) are counteracted by the inertia of the .housing (146-147) and the elasticity of bar 142. This, then, causes the housing (146-147) to oscillate in opposition to the pistons. The oscillation of the housing (146-147) is coupled to and delivered to the oscillatory drive shaft (bar 142).

The free-piston assembly comprising pistons 152-153 and their intermediate skirt portion 169 operate in phase opposition to the first-described assembly (154, 155, 166) to yield a balanced oscillatory drive about the axis of bar 142.

The annular skirt portion which interconnects piston 154 with piston 155 has a diameter which is greater than that of the major portion of the adjacent piston. This enlarged skirt functions as an intermediate piston which oscillates back and forth in cavities 171 and 172. These cavities (171 and 172) function as air springs which assist the return bounce of pistons 154 and 155 during each engine cycle. This auxillary air spring is not essential to the operation of the apparatus, but rather is an optional feature. Absent this feature, the cyclically opposed combustion sequence in entirely adequate to cause the piston assembly to oscillate (in combination with the resonant effect of bar 142).

Another ancillary feature of the construction shown in FIG. .11, is the scavenge. cylinder areas 162' and 163. As shown in FIG. 11, pistons 154 and 1.55 are each divided into twosections' of dissimilar diameter. The section of reduced diameter is located within the end of the cylinder adjacent the spark plug. The cylinder, being similarly stepped as to diamter, provides a scavenge area 162' (or 163') during a portion of the stroke of the piston assembly. When piston 154 (for example) moves in the direction opposite that of arrow 165, area 162 will be squeezed down so as to expel a volume of air through passage 161 into the opposite combustion chamber 163. This arrangement permits the engine to operate as a .two-cycle engine, not needing aseparate. valve train.

The combustion chambers are charged by means of spring valves 173 and 174 each of which opens on the back stroke of the corresponding piston. The back stroke pulls air through the venturi (e.g., venturi 158) so as to deliver a fuel-air mixture into passage 161. Then, on the next compression cycle of the volume communicating with passage 161, the mixture is forced into the combustion chamber in the end of the piston assembly at the opposite end of the free piston. Accordingly, each of the four pistons (152-155) function as a fuel-air charging means for the opposed end of each respective piston assembly.

The relative stroke of each free-piston assembly is a function of the combustion power, the cylinder porting, and other engine features determinative of the stroke of the piston. in actuality, the pistons can move through a considerably greater effective stroke than is the physical stroke dimension of the cylinder assembly. This accrues to the phasing and the freedom of motion of the cylinder housing, and its support, as well as that of the free-piston assemblies. The useful power in the system is developed by the dynamic reaction of the reversals of the piston motion. Thus, there is no need for connecting rods, crankshafts, and other apparatus of this type to couple the output energy into the transmission system. The simplicity of the present invention, as compared with conventional internal combustion engines, is an important feature thereof.

Power delivery in the system described above in connection with FIGS. 10 and 11, is essentially automatic and is responsive to inherent phase changes accruing to system operation. The phase of the piston motion can change in relation to the phase of the kinetic energy in the main resonating system. Variation in power can be made, as in a conventional engine, by varying fuel delivery to the combustion chambers. However, instead of having the pistons experience different torque conditions which is delivered via connecting rods to a crankshaft, the free pistons merely impart a dynamic reaction into the cylinder assembly, which then drive the resonator.

From the foregoing it can be seen that there is provided by the present invention a novel and greatly improved power system, such as may be used in vehicles, capable of providing a wide range of torque performance, a substantial reduction in friction, and a considerable reduction in cost owing to a greatly reduced total number of parts. Moreover, such parts as are required operate under more optimal conditions. There is no need for massive parts solely to deal with just momentary torque. And, in the combination of a free-piston engine and a shifting-node sonic transmission, the need for a separate oscillator driven through rotary shafts by a conventional prime mover, is eliminated. Thus, there is provided a basic simplicity wherein periodic combustion delivers the periodicity required for the torsional oscillation of the resonant transmission.

What is claimed is:

1. A rotary kinetic power system capable of maintaining a given relationship, one selectively established, between a commanded power level at the systems input and the power level extant at the systems output, comprising:

dynamic reaction means, having a selectively variable impedance for continuously generating selectively variable torsional vibrations;

means for converting cyclically reversing torsional vibration energy into a unidirectional turning I force;

a variable rotary mechanical load having an impedance that varies directly with the load torque;

means for connecting said converting means to said load whereby unidirectional turning force from said converting means is applied as a torque to said load; and,

impedance transforming means connected between said generating means and said converting means for inductively coupling said torsional vibrations therebetween, whereby said torsional vibrations are converted into a unidirectional turning force, having a torque that varies with changes in the ratio of the impedances between said generating means and said load.

2. A rotary kinetic power system as defined in claim 1 wherein said impedance transforming means comprises:

a torsionally resonant elastic bar. 3. A rotary kinetic power system as defined in claim 1 wherein said generating means comprises:

a selectively variable speed free-piston engine.

4. A rotary kinetic power system as defined in claim 2 wherein said generating means comprises:

a free-piston engine symmetrically mounted with respect to the axis of said bar whereby the cyclical motion of the free piston therein imparts a tangential force to said bar and thereby generates said torsional vibrations therein.

5. A rotary kinetic power system as defined in claim 4 wherein said free-piston engine comprises:

a pair of piston and cylinder assemblies mounted in opposition for angular motion about the axis of said bar.

6. A rotary kinetic power system as defined in claim 2 wherein said bar comprises:

an elongated elastic shaft of circular cross section having a first end resiliently supported and drivingly connected to said generating means so as to permit torsionally resonant vibrations to be propagated therein.

7. A rotary kinetic power system as defined in claim 1 wherein said dynamic reaction generating means comprises:

an orboresonant swinging-weight oscillator; and

a selectively variable speed rotary motor drivingly connected to said oscillator.

8. A rotary kinetic power system as defined in claim 7 wherein said impedance transforming means comprises:

a reaction arm extending from said converting means whereby tangential motion imparted to said arm is converted to an angular motion coaxial with said turning force; and I a pair of opposed springs having their outermost ends connected to said oscillator and having their confronting ends connected to said reaction arm.

9. a rotary kinetic power system as defined in claim 1 wherein said converting means comprises:

a pair of oppositely-phased unidirectional clutches,

each drivingly connected to said impedance transforming means, and having their outputs connected in common to said load connecting means.

10. A rotary kinetic power system as defined in claim 9 including:

an inertial flywheel coaxially mounted with respect to said common connection of said clutches.

11. A rotary kinetic power system comprising:

an orboresonant swinging-weight oscillator for generating torsional vibrations:

a selectively variable speed rotary prime mover drivingly connected to said oscillator;

means for converting torsional vibrations into a unidirectional tuming force;

resonant spring means interposed between the output of said oscillator and the input of said converting means for transmitting torsional vibrations therebetween; and

means for drivingly connecting said converting means to a mechanical load whereby unidirectional turning force from said converting means is applied as a torque to said load.

12. A rotary kinetic power system as defined in claim 11 wherein said converting means comprises:

a pair of oppositely-phased unidirectional clutches, each being driven by said resonant spring means, and having their outputs connected in common to said load connecting means.

13. A rotary kinetic power system as defined in claim 12 including:

an inertial flywheel coaxially mounted for rotation with said load connecting means.

14. A rotary kinetic power system as defined in claim 11 wherein said resonant spring means comprises:

lever means extending from said converting means whereby a tangential force applied to said lever means will result in a torsional motion at the input to said converting means; and,

a pair of opposed helical springs having their outermost ends connected to said oscillator whereby they may be driven therefrom, and having their confronting ends drivingly connected to said lever means.

15. A free-piston engine and torsionally resonant power system, comprising:

a pair of cylinder assemblies symmetrically mountedin opposition for angular displacement about a common axis;

first and second free pistons each slideably mounted within a corresponding cylinder assembly, for imparting a reaction torque thereto about said common axis;

selectively variable means for cyclically energizing said first and second free pistons in mutual phase opposition, thereby generating a cyclical torsional vibration about said common axis;

means for converting torsional vibrations into a unidirectional turning force;

a torsionally resonant elastic bar interposed between the common axis of said cylinder assemblies and the input of said converting means for transmitting torsional vibrations therebetween; and,

means drivingly connecting said converting means to a mechanical load whereby unidirectional turning force from said converting means is applied as a torque to said load.

16. A power system as defined in claim 15 wherein said converting means comprises:

a pair of oppositely-phased unidirectional clutches,

each being driven by said bar, and having their outputs connected in common to said load connecting means.

17. A power system as defined in claim 15 wherein said resonant bar comprises:

an elongated elastic shaft of circular cross section having a first end secured to the common axis of said cylinder assemblies and supported with rotary freedom so as to permit elastic torsional vibrations to be efiiciently propagated therein.

18. A power system as defined in claim 15 including:

an inertial flywheel mounted for rotation with said load connecting means.

19. A vehicular power system including a torsionally resonant transmission, comprising:

a prime mover having a rotating mechanical output;

a first unidirectional clutch having its power input connected to the output end of said acoustic lever means for receiving torsional vibrations therefrom, and having a rotating output shaft;

a second unidirectional clutch, oppositely phased in rotation with respect to said first clutch, having its power input connected to the output shaft of said first clutch, and having a rotating output shaft; and,

means connecting the output shaft of said second clutch to a mechanical load whereby unidirectional turning force transmitted through said first and second clutches is applied as a torque to said load.

20. A vehicular power system as defined in claim 19 including:

a first inertial flywheel mounted for oscillatory torsional vibration with the input end of said acoustic lever;

a second inertial flywheel mounted for oscillatory torsional vibration with the output end of said acoustic lever, the inertial mass of said second flywheel being greater than that of said first flywheel; and,

a third inertial flywheel mounted for rotation with the output shaft of said first unidirectional clutch. 

1. A rotary kinetic power system capable of maintaining a given relationship, one selectively established, between a commanded power level at the system''s input and the power level extant at the system''s output, comprising: dynamic reaction means, having a selectively variable impedance for continuously generating selectively variable torsional vibrations; means for converting cyclically reversing torsional vibration energy into a unidirectional turning force; a variable rotary mechanical load having an impedance that varies directly with the load torque; means for connecting said converting means to said load whereby unidirectional turning force from said converting means is applied as a torque to said load; and, impedance transforming means connected between said generating means and said converting means for inductively coupling said torsional vibrations therebetween, whereby said torsional vibrations are converted into a unidirectional turning force, having a torque that varies with changes in the ratio of the impedances between said generating means and said load.
 2. A rotary kinetic power system as defined in claim 1 wherein said impedance transforming means comprises: a torsionally resonant elastic bar.
 3. A rotary kinetic power system as defined in claim 1 wherein said generating means comprises: a selectively variable speed free-piston engine.
 4. A rotary kinetic power system as defined in claim 2 wherein said generating means comprises: a free-piston engine symmetrically mounted with respect to the axis of said bar whereby the cyclical motion of the free piston therein imparts a tangential force to said bar and thereby generates said torsional vibrations therein.
 5. A rotary kinetic power system as defined in claim 4 wherein said free-piston engine comprises: a pair of piston and cylinder assemblies mounted in opposition for angular motion about the axis of said bar.
 6. A rotary kinetic power system as defined in claim 2 wherein said bar comprises: an elongated elastic shaft of circular cross section having a first end resiliently supported and drivingly connected to said generating means so as to permit torsionally resonant vibrations to be propagated therein.
 7. A rotary kinetic power system as defined in claim 1 wherein said dynamic reaction generating means comprises: an orboresonant swinging-weight oscillator; and a selectively variable speed rotary motor drivingly connected to said oscillator.
 8. A rotary kinetic power system as defined in claim 7 wherein said impedance transforming means comprises: a reaction arm extending from said converting means whereby tangential motion imparted to said arm is converted to an angular motion coaxial with said turning force; and a pair of opposed springs having their outermost ends connected to said oscillator and having their confrOnting ends connected to said reaction arm.
 9. a rotary kinetic power system as defined in claim 1 wherein said converting means comprises: a pair of oppositely-phased unidirectional clutches, each drivingly connected to said impedance transforming means, and having their outputs connected in common to said load connecting means.
 10. A rotary kinetic power system as defined in claim 9 including: an inertial flywheel coaxially mounted with respect to said common connection of said clutches.
 11. A rotary kinetic power system comprising: an orboresonant swinging-weight oscillator for generating torsional vibrations: a selectively variable speed rotary prime mover drivingly connected to said oscillator; means for converting torsional vibrations into a unidirectional turning force; resonant spring means interposed between the output of said oscillator and the input of said converting means for transmitting torsional vibrations therebetween; and means for drivingly connecting said converting means to a mechanical load whereby unidirectional turning force from said converting means is applied as a torque to said load.
 12. A rotary kinetic power system as defined in claim 11 wherein said converting means comprises: a pair of oppositely-phased unidirectional clutches, each being driven by said resonant spring means, and having their outputs connected in common to said load connecting means.
 13. A rotary kinetic power system as defined in claim 12 including: an inertial flywheel coaxially mounted for rotation with said load connecting means.
 14. A rotary kinetic power system as defined in claim 11 wherein said resonant spring means comprises: lever means extending from said converting means whereby a tangential force applied to said lever means will result in a torsional motion at the input to said converting means; and, a pair of opposed helical springs having their outermost ends connected to said oscillator whereby they may be driven therefrom, and having their confronting ends drivingly connected to said lever means.
 15. A free-piston engine and torsionally resonant power system, comprising: a pair of cylinder assemblies symmetrically mounted in opposition for angular displacement about a common axis; first and second free pistons each slideably mounted within a corresponding cylinder assembly, for imparting a reaction torque thereto about said common axis; selectively variable means for cyclically energizing said first and second free pistons in mutual phase opposition, thereby generating a cyclical torsional vibration about said common axis; means for converting torsional vibrations into a unidirectional turning force; a torsionally resonant elastic bar interposed between the common axis of said cylinder assemblies and the input of said converting means for transmitting torsional vibrations therebetween; and, means drivingly connecting said converting means to a mechanical load whereby unidirectional turning force from said converting means is applied as a torque to said load.
 16. A power system as defined in claim 15 wherein said converting means comprises: a pair of oppositely-phased unidirectional clutches, each being driven by said bar, and having their outputs connected in common to said load connecting means.
 17. A power system as defined in claim 15 wherein said resonant bar comprises: an elongated elastic shaft of circular cross section having a first end secured to the common axis of said cylinder assemblies and supported with rotary freedom so as to permit elastic torsional vibrations to be efficiently propagated therein.
 18. A power system as defined in claim 15 including: an inertial flywheel mounted for rotation with said load connecting means.
 19. A vehicular power system including a torsionally resonant transmission, comprising: a prime mover having a rotating mechanical output; an orbiting-weight torsionAl oscillator for converting uniform rotary motion into cyclical torsional vibrations; gear drive means interposed between said prime mover and said oscillator for transmitting rotary power from said prime mover to said oscillator; acoustic lever means having an input end connected to the output of said oscillator, and an output end; a first unidirectional clutch having its power input connected to the output end of said acoustic lever means for receiving torsional vibrations therefrom, and having a rotating output shaft; a second unidirectional clutch, oppositely phased in rotation with respect to said first clutch, having its power input connected to the output shaft of said first clutch, and having a rotating output shaft; and, means connecting the output shaft of said second clutch to a mechanical load whereby unidirectional turning force transmitted through said first and second clutches is applied as a torque to said load.
 20. A vehicular power system as defined in claim 19 including: a first inertial flywheel mounted for oscillatory torsional vibration with the input end of said acoustic lever; a second inertial flywheel mounted for oscillatory torsional vibration with the output end of said acoustic lever, the inertial mass of said second flywheel being greater than that of said first flywheel; and, a third inertial flywheel mounted for rotation with the output shaft of said first unidirectional clutch. 